Grinding machine



Aug. 7,1934. H. ERNST Er A1. 1,969,063

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' i GRINDING MACHINE File@ Nov. 22, 1928 5 Sheets-Sheet 4 l z y Swanton:

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GRINDING MACHINE Filed Nov. 22. 1928" 5 sheets-sheet 5`IIIIIHIlHIIllIIIIHIIIIHIIIII u l HA/vs ER NST, HERMA/v RISLER,

Patented ug. 7, 1934 n UNITED sTATEs GRINDING MACHINE Hans Ernst andHerman R. Isler, Cincinnati,-

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Ohio, assgnors to Cincinnati Grinders Incorporated, Cincinnati, Ohio, acorporatioxrof Application November 22, 1928, Serial No. 321,198

37 Claims.

This invention relates to improvements in grinding machines/andparticularly to that type of grinding machine in which the work is heldbetween centers in opposition to a grinding 5 member for removal ofstock therefrom.

In the performance of grinding of this nature there are two generalmethods of grinding employed, one in" which the grinding wheel is feddirectly into the work and commonly known Al as plunge cut grinding andthe other in which a relative transverse movement is imparted to thework and grinding wheel to cover work of greater length than the widthof the wheel and in which the feeding action takes place only at l theend of the stroke or strokes of movement.

One of the principal objects of the present invention is the provisionof an improved automatic machine of universal application and capable ofutilization for either of said types of grinding.

A furtherv object of the invention is the provision of novel andimproved automatic or semiautomatic control mechanism for effecting thevarious desired movements of the parts of the machine.

An additional object of the invention is the provision of a machinewhich obviates the necessity for a large number of gears, clutch membersand the like for accomplishing the various desired feeding movements andadjustment of the speed thereof and which will satisfactorily accomplishthe results hitherto attained by gear mechanisms through the utilizationof a novel hydraulic control system therefor.

Further objects of the invention include the provision of improvedhydraulic circuits and control mechanisms therefor for operation of thegrinding wheel head slide and for operation of the grinding wheel tableto insure properly timed and sequential movements of the several' parts.

Other objects and advantages of the present invention should be readilyapparent by reference to the following specification taken in connectionwith the accompanying drawings, forming a part thereof, and it will beunderstood that we may make any modifications in the structural detailsor combination and arrangement of parts hereinafter described within thescope of the appended claims without departing from or exceeding thespirit of the invention.

Figure l is a front elevation of a machine embodying the presentimprovements.

Figure 2 is a transverse Vertical sectional view thereof, taken as onthe line 2-2 of Figure 1.

Figure 3 is a diagrammatic view illustrating the several control systemsfor the machine.

Figure 4 is a fragmentary view partially in section illustrating theconnections for imparting reciprocating movement to a long table member.e

Figure 5 is a fragmentary end viewwith parts in section illustrating thearrangement of the electrical and mechanical starting and stoppingsystem.

Figure A6 is a sectional View as on line 6--6 of Figure 1 illustratingthe pump drive and speeding up mechanisms.

Figure 7 is a fragmentary view illustrating the manual adjustment of thevariable displacement pump.

Figure 8 is a fragmentary section of the view as on line 8--8 of Figure.7.

Figure 9 is a fragmentary transverse section as on line 9--9 of Figure 1showing the manual table adjustment mechanism.

Figure 10 is a horizontal section as on line 10-10 of Figure 1 showingthe hydraulic table drive control valve mechanism.

' Figure 11 is a similar view showing a different adjustment of thevalve with respect of the several ports controlled thereby.

Figure 12 is a fragmentary view of the valve control lever for shiftingthe parts shown in Figures 10 and 11.

Figure 13 is a fragmentary section through the intermittent table feedflutter valve indicated in Figure 3v of the drawings, and

Figure 14 is a section as on line 14-14 of Figure 10.

In the drawings in which similar characters of reference are employed todenote corresponding parts throughout the several views the number 25designates the main bed of the machine formed with the longitudinallyextending ways 26 and 27 which slidably support the Work table 28 formovement longitudinally of the bed to tra-verse the Work with respect tothe grinding wheel. The bed is further formed with a rearward extension29 having the Ways 30 slidably supporting the grinding wheel carriage 31which has journaled therein the counter-shaft 32 Iand grindingWheelspindle 33 bearing the grinding wheel 34.

'I'he main power for driving the grinding wheel and imparting thevarious movements to the table and wheel slide is preferably furnishedfrom a suitable prime mover such as the motor 35 having a shaft 36provided with a drive pinion 37 which through chain 38 drives shaft 39,from which a belt 40 transmits power to the shaft 32. 'Ihe couplingbetween shafts 32 and 39 is such that the necessarily limited back andforth movement may be given the wheel slide Without effecting the driveof the parts, due to the swinging of belt 40 about shaft 39 as a centerduring such adjusting movement. In addition a chain or other driveconnection 41 extends forwardly into the bed 25, driving sprocket lo-theconstant displacement pump 53.

42 for actuation of the pump members, which control the hydraulic.actuating circuits for the respective slides. This drive includes acoupling clutch 43 by which power is transmitted from pinion 42 to shaft44 provided with the drive pinion 45 and the clutch face 46. Drivepinion 45 in turn actuates gear 47 of sleeve 48 journaled on the stubshaft 49 and having a pinion 50 normally in mesh with gear 51 on shaft52 of Disposed coaxially with shaft 44 is shaft 55 of the variabledisplacement pump 56 which controls the movement of the table at avariable rate dependingV upon the rate of flow through said pump. Thisshaft has a splined portion on which is slidably mounted gear 54 havinga spool 58 engaged by shifter yoke 57 actuable by handle 57 on the frontof the machine. When shifted to the left clutch face 59 on gear 54inter-engages with clutch face 46 on shaft 44 to drive the variabledisplacement pump at its normal rapid rate. To enable the rate ofactuation of the pump to be slowed down and thus permit a ne adjustmentof slow table traverse movements such as desirable for example, inperforming 'truing operations, gear 54 may be shifted to the right asindicated in Figure 6 to mesh with pinion 50. It will be understood thevariable displacement pump may be of any standard commercial type andpreferably such that a lateral displacement or variation in ecoentricityof the rotor will serve A to vary the rate of flow therethrough. Thisdisplacement may be controlled by a rotary actuating cam 60 operatedthrough miter gears 61 and knurled Wheel 62 projecting from the front ofthe machine, and provided with an indicator point 63 cooperating with adial 64 on the control plate of the machine for indicating theadjustment thereof.

'projecting fromthe front of the machine and is carried by-sleeve 68pivoted to one arm of the bell crank lever 69 secured as at 70 to thecontrol plate 71. The other arm of the bell crank carries a roller 72riding in slot 73 of plunger 74 which projects upwardly from controlplate 71 adjacent the edge of the table and is adapted to be depressedby the reversing dogs 75 just prior to the engagement of the reverse dogwith the table reverse lever 76.

The general normal cycle of operation of the table should be bestunderstood by reference to diagrammatic view in Figure 3 considered inconjunction with the valve structural details particularly brought outin Figures 10, 11 and 12.

'I'he table itself is shown as provided with the rack 77 on its undersurface having eshing therewith the drive gear 78 which isselectivelyrotatable either manually by pinion 79 or power actuated by cooperativeengagement of piston rack 80 with gear pinion 81. Rack 80 is carried bythe ends of the double piston rodv 82 intermediately provided withpiston 83 movable in cylinder 84. The purpose of this specicconstruction is to multiply the movement imparted to the table so thatthe mechanism may satisfactorily be employed on long beds requiringmaximum stroke of the grinding table, in

that a limited movement of piston 83 transmitted through rack 80 andpinion 81 to4 gear 78 will cause a much greater degree of movement ofthe grinder table.

It will of course be understood that while this multiplying mechanismhas been shown as most advantageous, if a lesser degree of movement ofthe table is desired, the piston may be coupled direct with the grindertable and the cylinder 84 carried by the bed of the machine.

In either event the hydraulic actuation is the same in that the.hydraulic conduits 85 and 86 are coupled with theI respective ends ofthe cylinder, the hydraulic circuit extending through valve casing 87including reversing valve 88 to the lower supplemental portion of thecasing containing starting and stopping valve 89 controlling pressureconduit 90-k and exhaust 91. In the normal operation of the machine,pressure of the desired amount is created by the constant displacementpump 53 and -is transmitted through conduit 90 to control valve 89. Whenin the position shown in Figure 11 this valve. will short circuit thepressure flow back through line 91 and an equalized pressure will actthrough lines 85 and 86 against opposite ends of the piston. When thevalve is moved to starting position, however, as shown in Figure 10 anddiagrammatically illustrated in Figure 3, the pressure ilow from theconstant displacement pump will be through conduit 90 valve 89 andconduit 86 to the right hand end of the piston cylinder creating an urgeof the piston toward the left. At the same time conduit 85 will becoupled through valve 88 and valve 89 with conduit 91 leading to thevariable displacement pump 56, the rate of discharge from the left handend of the cylinder being therefore positivelycontrolled by the rate ofpassage of fluid through the variable displacement pump providing alocked system positively and definitely controlling the table movementof the machine.

It will of course be understood that suitable provision is made toprevent building up of undue pressure in either side of the hydrauliccircuit. 'I'his may be accomplished by introduction of relief valve 92in the pressure side of the circuit and a corresponding emergency reliefvalve 93 in the branch conduit 94 extending to the oil or hydraulicfluid reservoir 95 from a point in the return line ahead of the variabledisplacement pump.

It will be noted that in normal operation the variable displacement pumptransfers the liquid from the discharge side 91 to the pressure side 90thus causing a continuous circulation of oil within the closed systemand with a pressure on the actuating or urge side in excess of that onthe opposite side due to the action of the constant displacement pump.The reversal of direction of actuation, as has been mentioned, isdetermined by contact of the table dog 75 with the reversing lever 76while the slowing down at the end of the table stroke prior to said-reversal is effected as by actuation of plunger 74, operating shiftscrew 65 to shift the variable displacement pump to a more nearlyneutral position, thus reducing the flow through the discharge line.

Considering now the mechanism for producing proper feeding of thegrinding wheel toward the work piece 95 when held between the head stock96 and tail stock 97 on the work supporting slide or table, reference ismade to diagrammatic view Figure 3 considered particularly inconjunction with the sectional view, Figure 2. From these views it willbe noted that the grinding wheel head or slide 31 has a depending arm 98provided with a bushing 99 in threaded engagement with screw 100. Thisscrew has pinned thereon piston 101 movable in cylinder 102 in anaxialdirection and also capable of rotation with the screw as effectedthrough the series of gears 103 operable from the front of the machineby hand adjusting wheel 104 and shaft 105. This rotation serves to movethe grinding wheel slide back and forth with respect to the piston incompensation for wheel wear and the like and to vary the position of thegrinding wheel slide for reciprocations of a given amplitude asdetermined by the stroke of the piston 101. The hydraulic actuatingsystem for the piston includes a conduit or passage 106 for conductingthe actuating fluid to the front of the piston to retract the wheel andslide and a second conduit 107 to conduct the actuating fluid into therear of cylinder 102 to forwardly urge the piston therein. .Theactuating fluid for this urge is supplied from the general pressure line90 fed by pump 53 through the pipe 108 as shown in Figure 2. A controlvalve casing 109 regulates the distribution of the actuating fluid toone end of the cylinder and its escape or discharge from the oppositeend thereof. For example with the valve in the position showndiagrammatically in Figure 3 and in full lines in Figure 2, the

pressure side of the system is coupled through conduit 108, valve 110and conduit 107 with the rear of cylinder 102 forwardly urging thepiston. At the same time the front or relief side is coupled throughconduit 106, valve 110 and pipe line 111 with the throttle valve 112allowing discharge of the fluid through discharge line 113 to reservoir95. 'I'he setting of the throttle valve determines the rate ofescapement of the fluid and thus the speed of movement of the wheeltoward the work. As an alternative proposition the valve 110 may bemoved one step toward the right coupling line 106`direct with line 113and thus permitting of rapid escape of the iiuid at the front of thepiston cylinder and consequent rapid movement of the wheel toward thework. Similarly a complete forward or left-hand movement of the valvewill couple pressure line 108 with the right hand branch 106' of passage106 introducing the actuating fluid to the front of the piston toretract the wheel and at the same time couple line 107 direct withdischarge passage 113 permitting this movement to be rapidly effected.Considering specifically the mechanism for automatic control of theseseveral movements of the grinding wheel attention is invited to the factthat valve 110 has a forwardly extending operating rod 114 adjustablycoupled by link 115 with the control handle 116 pivoted to the frontplate 71 of the machine.

Handle 116 has the inwardly extending bell crank arm 117 carrying thepawl 118 for securing the lever in desired adjusted position. A spring119 urges the bell crank arm downwardly and thus the main portion of thehandle inwardly toward the bed of the machine. In its most inwardposition the link 115 and thus rod 114 and valve 110 are moved towardthe lrear coupling pressure line 108 through the valve with passage 106and thence through 106 directing the actuating fluid toward the forwardside of piston 101. This pressure tends to rearwardly actuate the pistonand consequently the wheel head slide. At the same time passage 107 iscoupled through the valve 110 with the direct return line 113 permittingrapid rearward movement of the piston and wheel slide. This movementcontinues until flange or disc 120 on screw 100 contacts with the upperend of the intermediately pivoted lever 121 having a lost motionconnection as at 122 with valve rod 114. As the parts inter-engage thecontinued rearward movement of flange 120 will transmit forward movementthrough rod 114 to valve 110 shifting the valve to such a point that thecontrol pistons or flanges thereon simultaneously shut off the flow offluid under pressure to the front of the piston and the discharge fromthe rear. In other words the valve will occupy a stop positionpreventing movement of the'wheel head slide in either direction and atthe same time lever 116 will be rocked slightly forward. At this time'the operator can withdraw4 the completed Work piece from theworksupporting slide for table and insert a newv work piece. Thisoperation having been performed, by manual grasping and forward rockingof lever 116 the valve is moved to its extreme forward position. In thisposition the valve couples the pressure line 108 with passage 107 forforward actuation of the piston and wheel slide. At the same time thepassage 106 is coupled with the open return line 113 permitting rapidinward feeding of the grinding wheel 34. As the handle is so moved,locking pawl 118 is retracted permitting latch member 123 under urge ofspring pressed plunger 124 to move into a position over-lying stop 125when the pawl 118 will inter-engage with shoulder 126 on the latch,locking the lever in this forward position against the action of spring119.

It will be noted that the keeper is coupled by link 127 with the'lowerendof intermediately pi'voted lever 128 whose upper end extends into thepath of movement of the adjustable abutment 129 on the forward end ofscrew 100. Consequently as the wheel head slide and screw move forwardthe abutment will contact with the upper end of the lever swinging thelower end toward the rear of the machine and through link 127withdrawing the keeper from engagement with the handle locking pawl.When this takes place the pawl will drop down on its stop 125, occupyingthe position shown in Figure 2 of the drawings. It is to be understoodthat a corresponding movement of the lever 116 takes place, shifting thevalve 110 sufliciently to the rear to shut oil' flow through pipe 113and directing same through line 111 containing the throttle valve 112reducing the amount of flow so that the proper slow feed of the grindingwheel now ensues. The wheel will then be fed into the Work to the limitof movement of the slide as determined by interengagement of the end ofthe screw with stop bracket 130 where the parts will remain until handle116 is manually shifted to reverse the valve and cause the retraction ofthe wheel head slide as previously described. It will be noted thatabutment 129 is adjustable with respect to screw as for initialpositioning of the machine to cause the tripping out action slowing downfrom rapid advance to feed to take place a predetermined distance beforethe grinding wheel slide reaches its limit of movesupporting pivot andthus the point at which upper end of lever 128 will contact withabutment 129 andv become effective to automatically change the wheelhead speed from rapid advance to slow feeding action.

'I'he complete cycle of wheel head control mechanism just described isparticularly adapted for in-feed grinding, which is to say grinding inwhich the work is stationary and the wheel is continuously fed directlyinto the work for the desired depth of cut. When the machine is utilizedfor traverse grinding or grinding in which the work or Work tablereciprocates a different system of feed is required in that the wheelhead is preferably given a limited amount of inward feed at each end ofthe table stroke and held in this position during the traverse of thework so that an equal amount of stock is removed circumferentially ofthe work throughout its length at each table stroke. To control theinward feed in this system ofgrind ing, line 111 is provided with a twoWay cock 136 which in one position directs the flow through throttlingvalve 112 into the exhaust or reservoir line 113 and in its otherposition directs the flow through conduit 137 which discharges intosupplemental valve casing 138 containing valve 139, preferably as anintegral continuation of valve 88. Casing 138 has ports 139 and 140communicating through lines 141 and 142 with the termini of escapementcylinder 143. This cylinder contains the shuttle piston or flutter valve144 whose stroke is limited by abutment 145 on adjusting screw 146having a knurled -operating head 147 projecting on the front plate 7l.The head is further provided with a dial 148 cooperating with amicrometer indicator 149 for determining the effective adjustment ofabutment 145. Valve casing 138 is further provided with a portcommunicating with pipe 149 and a second port communicating with itsbranch 149 pipe 149 being continued over and discharging -into line 113.

In the operation of this mechanism Valve `88, being coupled with thetable reverse lever 76, is reciprocated at each end of the table stroke.This correspondingly reciprocates valve 139 to alternately couplepressure inlet 137 with ports- 139' and 140 and at the same time toalternatively couple discharge line 149-149 with the other of theseports. Considering the back pressure or discharge fluid from the forwardend of cylinder 102 as entering cylinder 143 through pipe 142, shuttlepiston 144 will be forced toward the left as indicated to an amountlimited by the position of abutment 145, thus allowing a predeterminedamount of said fluid to enter the right hand end of the cylinder. -Whenthe valve is reversed 142 will then be coupled with discharge line149-149 and the pressure oppositely admitted through 141. As line 149 isunder atmospherical pressure against the duid in the reservoir only, themeasured amount of fluid previously admitted to the right i of cylinder143 will be forced therefrom by movement of piston144 to the right and acorresponding amount will be permitted to enter the left hand end of thecylinder. The wheel head can then advance toward the work to the extentof the reduction in amount of uid thus escaping from the forward end ofcylinder 102. I'his operation -is repeated at eachA reversal of thetable until the wheel reaches its forward limit of movement. It willthus be seen that the piston 144 by its movement in the cylindermeasures out the back pressure fluid from the main wheel head shiftingcylinder, allowing the wheel to advance toward the work by prescribedincrements whose amount is determined by the adjustment given toabutment 145 and that consequently there is a forwarding movement ofdesired amount imparted to the `wheel at each reversal of the tablecontrolling valve.

It will of course be understood that the -reversal of the table may beeffected either manually, or automatically by actuation of lever 76 onrock shaft 150 which is provided with the double end detent cam 151cooperating with the notches 152, 153 in the pair of actuating arms 154which are urged together by the spring 155 and serve as the lever isrocked to snap it from one position to another and lock it in desiredadjusted position. The connection between the lever and the valve proper88 includes the rock arm 156 and actuator 157 engaged in slot 158 ofhead 159 on rock shaft 150. There is a lost motion between these partspermitting of initial movement of -the lever under influence of theappropriate table dog without shifting of the Valve coupled with asudden impact positively throwing the valve from one position to theother if the lever and associate parts are swung under the influence.

control arm 161, movement of member 161 in one direction initiating thetable traverse and in theI opposite direction producing a balancedpressure condition as previously described holding the table againstmovement for direct infeed grinding. In addition, the entire movement ofthe table and wheel-head slide as well as rotation of the work may bestopped through the use of the combined starting control lever 162 onrock shaft 163 which extends into the bed and carries the shifter arm164 operating clutch shifter yoke 165 engaging spool 166 of clutch 43for shifting same for disconnecting the drive to the parts from maindrive sprocket 42 as particularly illustrated in Figure 6. Rock shaft163 in addition carries the actuating arms 167-168 for the starting andstopping switch plungers 169 and 170 respectively. 4These plungerscontrol the circuit of motor 171 which drives the head stock 96 so thaton shifting of the lever in one direction the motive power for the headstock will be stopped by breaking of the electric circuit therefor andsimultaneously therewith power drive will be disconnected from theconstant and variable delivery pumps preventing further hydraulicactuation of the machine. Under these conditions it will be evident thatthe main Vdrive motor 35 may be left in operation or that the circuittherefor may also be coupled with the switch plungers 169 and 170 forcomplete control of the actuation of the machine from the single lever.as may be preferred.

As was mentioned above the work table 28 may be reciprocated manuallywhen the pinion 79 is shifted into engagement with gear '1 8.

vThe pinion 79 is provided with a groove 175 in which is received ashifting shoe 176 carried by control arm 161. This control arm 161 ispivotally connected to lever 177 which controls the movement of thestarting and stopping valve -89 as well as the shifting of gear pinion'79 on shaft '78 into and out of engagement with gear 78. Shaft 178 hasa gear connection 179 with hand wheel 180 whereby the table may bemanually shifted across the face of the grinding wheel.

From the drawings it will be noted that the manual means and the powermeans for reciprocating the table are never simultaneously in operatingconnection, but that when the lever 177 is actuated about its pivot 181toward the bed of the machine the manual means are disconnected and thepower means connected, and conversely, when the lever is moved away fromthe bed manual means is connected and the power means disconnected.

From the foregoing description the general operation of the presentimproved hydraulically controlled grinding machine should be readilyunderstood and it will be seen that there has been provided a machineparticularly adapted for either traverse or plunge cut grinding purposesin which the maximumv length of table movement may be effected withminimum length of piston or piston rod parts; in which the rate oftraverse of the table when utilized for traverse grinding may be readilyvaried within wide limits and with a smooth and uniform movement inwhich extreme smoothness of reversal of the table may be effected due tothe automatic slowing down of the rate of table movement prior toactuation of the automatic re-E versing mechanism therefor; and in whichthe rate of relative feeding movement between the grinding wheel andwork may be automatically hydraulically controlled and properlyaccurately effected at the end of each relative traversing stroke of theparts.

It will further be noted that an improved semi-automatic cycle ofgrinding Wheel movement has been provided which is equally adapted foruse in conjunction with both forms of grinding and which serves to causea rapid relative approach of the grinding wheel and work, followed by aslow feeding movement of properly controlled nature and an ultimatelimitation of the feeding movement suceeded if desired by an automaticrapid separating of the parts when the prescribed grinding has beencompleted. Y

It will further be noted that the various unitary portions of themachine such as the feeding and retraction of the grinding wheel, thetrav- 1 ersing movement of the table, the rotation or drive of the headstock may be independently controlled and 'started or stopped as desiredor in which the functioning of all of said parts and the drive of thegrinding wheel itself as Well may g be started or stopped by a singlecontrolling member therefor.

-It is also to be noted that a machine has been provided in which theessential operations such as the relative feeding and retraction of workand grinding wheel in a direction controlling the amount and rate ofstock remdval, and the relative traversing of the parts to control theextent of surface operated upon are all"hydraulically effected by asingle pressure pump or source of power while individual rate.controlling means are provided governing the action of the ,severalparts under impulse received from the common source of power. l

We claim:l

1. A- grinding machine including a bed and a wheel slide movable on thebed, hydraulically actuable means for shifting the slide on the bed. acontrol valvefor determining the rate and direction of movement of theslide on the bed,

a trip actuable means for automatically shifting the valve to reduce therate of movement of the wheel slide in one direction, a manual means foradditionally shifting the valve to reverse the dircction of movement ofthe slide, and additional trip controlled means actuable on said reversemovement of the slide for automatically shifting the valve to check allmovements of the slide.

2. A grinding machine including a bed and a wheel slide movable on thebed, hydraulically actuable means for shifting the slide on the bed, acontrol valve for determining the rate vsaid reverse movement of theslide for automatically shifting the valve to. check all movements ofthe slide, and manually operable means for adjusting the position of theslide with respect to the hydraulic actuating means and trip controlstherefor, whereby 'the position of Athe slide is varied for tripcontrolled reciprocations of the same amplitude.

3. A grinding machine including a bed, a work supporting tabletranslatable on the bed, a grinding wheel slide movable on the bed in adirection toward and from the table, hydraulically operated means forimparting a reciprocating movement to the table, additionalhydraulically operable means for moving the wheel slide in a directiontoward and from the table, common means for supplying actuating fluid tosaid hydraulically actuable mechanisms, a variable displacement pump inthe table hydraulic circuit for controlling the rate of discharge ofsaid circuit and consequently the rate of movement of the table, andindependent throttling means in the grinding wheel slide hydrauliccircuit for variably determining the maximum rate of discharge of saidcircuit and consequently the rate of movement of the grinding wheelslide.

4. A grinding machine including a bed, a work supporting tabletranslatable on the bed, a grinding wheel slide movable on the bed in adirection toward and from the table, hydraulically operated means forimparting a reciprocating movement to the table, additionalhydraulically operable means for moving the wheel slide in a directiontoward and from the table, means for supplying actuating fluid to saidhydraulically actuable mechanisms, a variable displacement pump in thetable hydraulic circuit` for co'ntrolling the rate of movement of the"table, an independent throttling means in vthe grinding wheel slidehydraulic circuit for variably determining the maximum rate of movementof the of, and additional means for varying the speedv grinding wheelslide, a supplemental hydraulic return line 4for the grinding wheelcircuit and meansA for selectively completing the circuit inclusive orexclusive of the throttling device to vary the rate of movement of saidslide.`

5. A grinding machine including a bed and table reciprocably mountedthereon, a grinding wheel on the bed, means for imparti relative feedingmovement to the grinding w el and table to determine the rate of stockremoval from a work piece on the table, an hydraulically operablemechanism for .effecting said relative movement including acylinder andcontained piston one of said partsA being secured to the bed and theother to a movable member, a'hydraulic circuit for introducing actuatinguid into one end of the cylinder and conducting it from the opposite endof the cylinder, an escapement mechanism in the discharge line, andmeans for eiecting actuation of the escapement mechanism as the tablereaches a prescribed limit by movement in one direction.

6. An hydraulically actuated grinding machine including a bed, a tablereciprocable thereon, means for hydraulically reciprocating the tableincluding a cylinder and piston intermediately f movable in thecylinder, one of said parts being rigidly secured to the bed and theother operatively associated with the table, and means for controllingthe relative movement of piston and cylinder and thus movement of thetable on the bed comprising a hydraulic circuit including a constantdelivery pump for supplying actuatingr iluid to one end of the cylinderand a variable delivery pump controlling the flow of fluid from theopposite end of the cylinder, means for varying the rate of flow ofiiuid through the variable delivery pump at a given speed of rotationthereo! rotation of said variable delivery pump.

'7. An hydraulically actuated grinding machine including a bed, a tablereciprocable to decelerate the rate of translation of the movablemember. prior to reversal thereof.

10. A grinding machine mechanism including a bed or support and a slidemovable thereon, a piston rod coupled with the slide for a'ctuationthereof, a piston coupled with the-rod, a rate and direction determiningvalve for controlling the movement of the piston, releasable means-forlocking the valve in position for rapid actuation of the piston in onedirection, means for shifting the valve to decelerate the rate ofmovement of the slide and a controlling device extending into the pathof movement of the piston rod and engageable thereby to render saidvalve shifting means operative.

11. In a machine of the character described, the combination with a bedor support, of a wheel head carriage slidably mounted thereon, a pistoncoupled with the carriage, an hydraulic system for actuating the pistonin reverse directions including a single control valve for varying therate and direction of movement of the carriage, means for shifting thevalve to initiate the movement of the piston in a given direction at agiven rate, means for resiliently actuating the valve to reduce the rateof movement of the carriage in said given direction means for lockingthe valve against said resilient actuation, release mechanism operableby thereon, means for hydraulically reciprocating rmovement 0f thecarriage to disengage the lockthe table including a cylinder and pistonintermediately movable in the cylinder, one of said parts being rigidlysecured to the bed and the other operatively associated with the table,and means for controlling the relative movement of piston and cylinderand thus movement of the table on the bed comprising an hydrauliccircuit including a constant delivery pump for supplying fluid to oneend of the cylinder and a variable delivery pump controlling the ilow offluid from the opposite end of the cylinder, means for automaticallyreversing the coupling of the constant and variable delivery pumps withthe cylinder to reverse the direction of movement of the table, andmeans for automatically decreasing the flow of fluid through thevariable delivery pump prior to the action of said reversing means.

8.` A grinding machine of the character described including a bed, atable reciprocable on 4the bed, a grinding wheel movable toward and ingmechanism whereby resilient actuation of the valve is effected,adjustable means for determining the timing of said release with respectto the movement of the carriage, and means for shifting said valve toreverse the direction of movement of the piston and carriage.

12. In agrinding machine, the combination with a bed or support, of aWork supporting member, a wheel supporting member, said parts beingmounted for relative feeding movement to produce proper stock removalfrom the Work piece, and means for controlling said relative feedingmovement comprising an hydraulic system including a pistonintermediately mounted in a double end cylinder, means for supplying anactuating medium to one end of the cylinder, a discharge conduitextending from the opposite end of the cylinder, and a measuring devicefor controlling the escape of actuating medium through the conduit,including a cylinder, a shuttle member therein, and means foralternately directing the escaping iluid to the opposite ends of thecylinder whereby the cubical displacement o'f the shuttle memberdetermines the increments of escape of the iiuid through the conduit.

13. In a grinding machine, the combination with a bed or support, of awork supporting member, a wheel supporting member, said parts beingmounted for relative feeding movement to produce proper stock removalfrom the work piece, and means for controlling said relative gfedingmovement comprising an hydraulic system including a pistonintermediately mounted in a double end cylinder, means for supplying anactuating medium to one end of the cylinder, a discharge conduitextending from the opposite end of the cylinder, a measuring device forcontrolling the escape of actuating medium through the conduit,including a cylinder, a 'shuttle member therein, and means foralternately directing the escaping uid to the opposite ends of thecylinder whereby the cubical displacement of the shuttle. memberdetermines the increments of escape of the fluid through the conduit,and means for variably determining the amount of movement of the shuttlemember to vary the amplitude of individual feeding movements ascontrolled thereby.

14. A cylindrical grinding machine including a. bed or support, a workholding table mounted on the support for translation relative thereto, agrinding wheel carriage slidably mounted on the support for feedingmovement toward and from the work support, and an hydraulic controlsystem for said parts including a common source of actuating uid for theslide and table, a variable displacement return pump for controllingreturn of actuating fluid and thus the rate of movement of the tabletransversely of the grinding wheel, an actuating piston for the grindingwheel carriage, and a plurality of selectively couplable controlmechanisms for said rpiston including a fluid escapement conduit, althrottle controlled conduit and an escapement mechanism, whereby rapidadvance or return of the grinding wheel, slow or intermittent movementthereof may be effected.

15. A cylindrical grinding machine comprising a work support, arotatable grinding wheel, a grinding wheel slide therefor, a cross feedscrew operatively connected to the slide, manually operable mechanismfor turning the cross feed screw to feed the grinding wheel into thework, a fluid pressure mechanism including a motor operatively connectedto move the screw bodily endwise and quickly move the wheel towards thework, and a stop to locate the wheel adjacent to the work.

16. A cylindrical grinding machine comprising a work support, arotatable grinding wheel,

-a grinding wheel slide therefor, a cross feed screw operativelyconnected to the slide, manually operable mechanism for turning thecross feed screw to feed the grinding wheel into the work, a fluidpressure mechanism including a, motor operatively connected to move thescrew bodily endwise and thereby quickly position the wheel adjacent tothe work, said motor having a movable part connected to the screw, meansincluding a stop for limiting the endwise movement of said screw in onedirection, and means for so controlling said fluid pressure mechanism asto maintain a constant pressure on said stop to hold the feed screwagainst endwise movevment while the same is being turned to effect thegrinding feed.

17. In a machine tool organization the. combination of a bed, a toolcarriage mounted thereon for movement relative thereto including a screwrod, means for rotating the screw for effecting adjustment of thecarriage, hydraulic means for axially shifting the screw rod foradjusting the position of the carriage relative to the bed, saidhydraulic means being adapted to shift the carriage at rapid and slowrates in sequential order, and trip means for changing the rate ofmovement of the carriage.

18. In a grinding machine of the class described the combination with abed, and a grinding wheel carriage mounted thereon for movement relativethereto, of hydraulic means for effecting said movement of the carriageat rapid and slow rates including a piston operatively connected withthe carriage, an hydraulic medium for shifting the piston, a conduit forthe medium, a valve for alternately directing the medium from theconduit to opposite ends of the piston and for connecting the other endof the piston with a throttled or an unthrottled return conduit, andtrip controlled means operable by the slide for shifting the valve todirect the exhaust medium successively through the unthrottled andthrottled discharge conduits.

19. In a grinding machine of the class described the combination with abed, and a grinding wheel carriage mounted thereon for movement relativethereto, of hydraulic means for effecting said movement of the carriageat rapid and slow` rates includingl a piston operatively connected withthe carriage, an hydraulic medium for shifting the piston, a conduit forthe medium, a valve for alternately directing the medium from theconduit to opposite ends of the piston and for connecting the other endof the piston with'a throttled or an unthrottled return conduit, andtrip controlled means operable by the slide for shifting the valve todirect the exhaust medium successively through the unthrottled andthrottled discharge conduits, comprising a valve stem extending from thevalve, a lever connected with the stem, yielding means tending toactuate the lever in one direction and shift the valve, a latchtensioning the yielding means, and means operable by the slide forreleasing the latch and thereby the yielding means.

20. In a grinding machine of the class described the combination with abed, and a carriage mounted thereon for movement relative thereto, ofhydraulic means for effecting said movement including a pistonoperatively coupled With the carriage, an hydraulic medium, means forcirculating the medium under pressure for actuating the piston, a valvefor connecting the medium alternately with opposite sides of the pistonfor reversely actuating the same, the valve connecting the idle side ofthe piston when moving in one direction for selective discharge throughan unthrottled or a throttled conduit, means for automatically shiftingthe valve to direct the exhaust medium sequentially through theunthrottled and throttled conduits including yieldable means forshifting the valve, a latch normally preventing movement of the valve bythe yieldable means, a trip operable by the carriage for releasing thelatch and the yieldable means. and means for varying the point at whichthe automatic shifting of the valve takes place including a screw shaft,a nut on 4the shaft to which the latch is pivoted, and means forrotating the screw.

21. In a grinding machine of the class described the combination with abed, and a carriage mounted thereon for movement relative thereto, ofhydraulic means for effecting said movement including a pistonoperatively coupled with the carriage, an hydraulic medium, means forcirculating the medium under pressure for actuating the piston, a valvefor connecting the medium alternately with opposite sides of the pistonfor reversely actuating the same, the valve connecting the idle side ofthe shifting the valve to direct the exhaust medium sequentially throughthe unthrottled and throttled conduits including yieldable means for 1shifting the valve,.a latch normally preventing lmovement of the valveby the yieldable means,

a trip operable by the carriage for releasing the latch and theyieldable, means, means for varying the point at which the automaticshifting of the valve takes place including a screw shaft, a nut on theshaft to which the latch is pivoted, means for rotating the screw, andindicating means for accurately positioning the latch.

22. In a grinding machine of the class described the combination with abed, and a Work supporting tablemounted thereon "for movement relativethereto, of hydraulic means for effecting the translation of the tablecomprising a piston and cylinder mechanism one of which is movable andthe other fixed, a rack adjustingv the rate of discharge of the variabledelivery pump for thereby varying the rate of movement of the table.

23. In afgrinding machine of the class described the combination Withabed, and a work supporting table mounted thereon for movement relativethereto, of hydraulic means for effecting the translation of the tablecomprising a piston and cylinder mechanism one of which is movable andthe other fixed, a rack movable with said movable member of the pistonand cylinder mechanism, a rack on the table, transmission gearingbetween the racks whereby the movement of the piston and cylinder rackis increased as table movement, an hydraulic pump connected with one endof said piston and cylinder mechanism for creating an hydraulic urge onthe movable member, a variable displacement pump connected with theother end of said mechanism for determining the rate of actuationthereof, means projecting beyond the forward wall of the bed foradjusting the rate of discharge of the variable delivery pump forthereby varying the rate of movement of the table, means for reversingthe connections of the pumps for reversing the movement of the table,and means for temporarily reducing the discharge from the variableliplacement pump prior to each reversal of the 24. In a grinding machineof the class described the combination with a bed, and a Work supportingtable mounted thereon for movement relative thereto, of hydraulic meansfor effecting the translation of the table comprising a piston andcylinder mechanism one of which is movable and the other fixed, a rackmovable' with said movable member of the piswhereby the movement of thepiston and cylinder rack is increased as table movement, an

hydraulic pump connected with one end of said piston and cylindermechanism for creating an hydraulic urge on the movable member, avariable displacement pump connected with the other end of saidmechanism for determining the rate of actuation thereof, meansprojecting beyond the forward wall ofthe bed for adjusting the rate ofdischarge of the variable delivery pump for thereby varying the rate ofmovement of the table, means for reversing the connections of the pumpsfor reversing the movement of the table, and means for temporarilyreducing the discharge from the variable displacement pump. prior toeach reversal of the table, said means comprising a depressible plungeroperable by the table, and a pump adjuster operatively connected withthe plunger.

25. A grinding machine comprising a base, a slidable table thereon, apiston and cylinder mechanism arranged to move said table, a fluidpressure system to admit fluid under pressure to either end of saidcylinder, a valve mechanism in said system arranged to control the rateof fluid flow in said system, and means actuated by movement of saidtable to operate said valve to diminish the fluid flow from saidcylinder when the table has'reached a predetermined position and therebycause the table to move thereafter at a definite but slower speed.

26. In a grinding machine the combination of a bed, a work supportingtable carried thereby and translatable longitudinally thereof, agrindingwheel carriage carried by the bed and movable transversely thereoftoward and from the Work supporting table, means for effecting saidtranslation including an hydraulic reciprocating motor, an hydraulicmedium for actuating the motor, means controlling the flow of themediiun to effect a movement of the carriage at a rapid rate, meanscontrolling the flow of the medium to actuate the carriage at a constantslow rate, means for controlling the flow of the medium to actuate thecarriage intermittently at a slow rate, means to automatically directthe flow of the medium from the rapid rate controlling means to eitherof the slow rate controlling means, and means for determining which ofthe slow rate controlling means is to be used.

27. In a grinding machine thev combination of a bed, a grinding wheelcarriage carried therebyv and movable transversely thereof, anhydraulically actuated reciprocating motor for effecting said movementof the carriage, an hydraulic medium for the motor, a valve controllingthe flow of the medium, manual means for shifting the valve to initiatea movement of the carriage at a rapid rate in one direction, meansoperable by the Acarriage for shifting the valve to slow down themovement thereof in the said direction and minutely adjustable means fordetermining the point at which the change in movement of the carriagefrom the rapid rate to the slow rate takes place.

28. In a grinding machine the combination of a bed, a grinding wheelcarriage carried thereby and movable transversely thereof, anhydraulically actuated reciprocating motor for effecting said movementof the carriage, an hydraulic medium for the motor, a valve controllingthe flow of the medium, manual means for Vshifting the valve to initiatea movement of the carriage at a rapid rate in one direction, meansoperable by the carriage for shifting the valve to slow down themovement thereof in the said direction, minutely adjustable means fordetermining the point at which the change in movementl of the carriagefrom the rapid rate to the slow rate takes place, and means for varyingthe slow feeding rate of movement whereby the grinding wheel may be fedinto the work at dierential rates.

`29. In a grinding machine the combination of a bed, a reciprocatingwork supporting table carried thereby, a grinding wheel carriage carriedby the bed movable transversely thereof toward and from the worksupporting table at a rapid rate and a slow feed rate, means forcontrolling the actuation of the carriage toward the table to feed thegrinding wheel into the work at a constant slow feeding rate, means forcontrolling the actuation of the carriage toward the table tointermittently feed the grinding wheel into the work, and means forsimultaneously connecting one of said feed controlling means with anddisconnecting the other from the carriage.

30. In a grinding machine the combination of a bed, a reciprocating worksupporting table carried thereby, a grinding wheel carriage carried bythe bed movable transversely thereof toward and from the work supportingtable at a rapid rate and a slow feed rate, means for controlling theactuation of the carriage toward the table to feed the grinding wheelinto the work at a constant slow feeding rate, means for controlling theactuation of the carriage toward the table to intermittently feed thegrinding wheel into the work, means for simultaneously connecting one ofsaid feed controlling means with and disconnecting the other from. thecarriage, and additional means for determining the rate of the slow feedmovement of the carriage when being constantly fed and the amount ofmovement of the carriage when being intermittently fed.

31. In a grinding machine of the class described the combination of abed, a slide mounted thereon for movement relative thereto at fast andslow rates in a given direction, hydraulic means for effecting themovement of the slide including a valve for controlling the speedthereof, a trip member carried by and movable with the slide, latchmeans in the path of movement of the trip member for holding the valvein one position, and yielding means for shifting the valve to a secondposition upon release thereof by the trip mechanism.

32. In a grinding machine of the class described the combination of abed, a grinding wheel carriage movable thereon at rapid and feedingrates through a given zone, hydraulic means including a valve foreffecting the movement of the carriage, latch means for holding thevalve in one position to effect the rapid movement of the carriage,yielding means for shifting the valve to a second position upon releaseof the latch means to eiIect the movement of the slide at a slow rate,trip means carried by the slide for releasing the latch, means forvarying the effectiveness of the latch means and thereby varying thepoint at which the change from rapid to slow takes place, and stopmeansl for limiting the reverse movement of the carriage.

33. In a grinding machine of the class de- :scribed the combination of abed, agrinding wheel carriage movable thereon at rapid and feeding ratesthrough a given zone, hydraulic means including a valve for effectingthe move- .lease of the latch means to effect the movement ment of thecarriage, latch means for holding the valve in one position to effectthe rapid movement of the carriage, 'yielding' means .for shifting thevalve to a second position upon reof the slide at a slow rate, tripmeans carried by the slide for releasing the latch, means for varyingthe effectiveness of the latch means and thereby varying the point atwhich the change from rapid to slow takes place, stop means for limitingthe reverse movement of the carriage, and means for changing the zonethrough which' the movement of the slide takes place without changingthe point in said zone at which the change in movement occurs.

34. In a grinding machine of the class described the combination of abed, a grinding wheel carriage mounted thereon for movement relativethereto at a continuous slow rate or at an incremental intermittentrate, hydraulic means for eiectingsaid movement of the carriage, a worksupporting table mounted on the bed for reverse translation relativethereto and for controlling the incremental intermittent feed of thecarriage, a valve in the hydraulic means 1N for determining whether thecontinuous infeed or intermittent feed is to be employed, a valve in thehydraulic circuit for determining the rate of the continuous feed, avalve in the circuit for determining the amount of incremental feed,means for effecting and determining the adjustment of each of saidvalves, and a valve casing carried by the bed for containing saidvalves.

35. In a grinding machine the combination of a bed, a grinding wheelcarriage carried thereby and shiftable relative thereto, an adjustingscrew having a threaded engagement with the carriage, the screw having asplined portion thereon,

a gear connected with the screw through the i splined portion wherebythe screw is rotated with the gear while the'screw may be axiallyshifted relative to the gear, a piston on the screw, and means forrotating the gear for adjusting the slide at a slow rate and forshifting the piston for moving the slide at a rapid rate independent ofthe movement thereof by the gear.

36. In a grinding machine the combination of a bed, a slide carriedthereby and movable relative thereto at a slow rate and at a rapidtraverse ratefa screw rod having a threaded connection with the slideadapted to be rotatably actuated for moving the slide at a slow rate, apiston carried by the screw rod adapted to be axially shifted for movingthe slide at a rapid rate, and means for actuating the screw rodrotatably and axially 1m at the proper rates.

37. In a grinding machine of the class described the combination of abed, a grinding wheel carriage mounted thereon for movement relativethereto, a work supporting table on the bed for supporting a work piecein the line of movement of the carriage, hydraulic means for effectingthev movement of the carriage at rapid and feeding rates toward thetable, and means for determining the point of change in speed of thecarriage comprising a member movable within the carriage, a tripmechanism in the line of movement of the member, latch means normallyholding the trip mechanism against operation, and yieldable meansoperable upon the operation of the trip mechanism to render the latchmechanism inoperative.

HANS ERNST. HERMAN R. IBLER. l.

